CN213574610U - Compressor and heat exchange system - Google Patents

Abstract

The application discloses compressor and heat transfer system, compressor include motor, casing and by pass line. The motor is arranged in the shell, the shell comprises an air inlet and an air outlet, and a circulation space for fluid to flow is arranged in the shell; the bypass pipeline comprises a first connector and a second connector which are arranged on the shell; the bypass pipeline is configured to transmit fluid from the second port to the first port; the motor includes the first end that is close to the air inlet and the second end that is close to the gas outlet, and first interface is located between the air inlet of the first end of motor and casing, and the second interface is located between the second end of motor and the gas outlet of casing. In the arrangement, the refrigerant which is positioned in the compressor and flows through the peripheral side of the motor can flow into the circulation space again through the bypass pipeline from the first interface and flow through the motor again, so that the motor is cooled for many times, the motor is prevented from being damaged due to overhigh temperature, and the compressor is protected.

Description

Compressor and heat exchange system

Technical Field

The application relates to the field of heat exchange, in particular to a compressor and a heat exchange system.

Background

The compressor in the heat exchange system, especially the screw compressor, is widely applied in the heat exchange system due to the advantages of large capacity, high unit efficiency, high reliability and the like. During the use process of the screw compressor, the rotating speed is high, the generated heat is high, so that enough oil drop lubrication is needed, and the requirement of the screw compressor on an oil drop lubrication system is also high.

However, when the compressor in the existing heat exchange system operates at the minimum load, the problem that the temperature of the motor is too high often occurs, so that the service life of the compressor is affected.

SUMMERY OF THE UTILITY MODEL

The application provides a compressor and heat transfer system, it can realize the protection to the compressor.

According to a first aspect of the present application, there is provided a compressor configured to compress a fluid,

the compressor includes:

a motor;

the motor is arranged in the shell, the shell comprises an air inlet and an air outlet, and a circulation space for fluid to flow is arranged in the shell;

the bypass pipeline comprises a first interface and a second interface, and the first interface and the second interface are arranged on the shell and communicated with the circulation space; the bypass conduit is configured to transfer fluid from the second port to the first port;

the motor comprises a first end close to the air inlet and a second end close to the air outlet, the first interface is located between the first end of the motor and the air inlet of the shell, and the second interface is located between the second end of the motor and the air outlet of the shell.

Further, the housing further comprises a rotor cavity and a motor cavity, the motor is arranged in the motor cavity, and the rotor cavity is communicated with the motor cavity and is far away from the air inlet relative to the motor cavity;

the second port is located in the rotor cavity.

Further, the compressor also comprises a screw assembly, and the screw assembly is arranged in the rotor cavity;

the screw assembly comprises a power input part and an extrusion compression part;

the projection of the second interface on the screw assembly is located an extrusion compression part, the distance from the projection to one end of the extrusion compression part close to the power input part is a first distance, and the ratio of the first distance to the length of the extrusion compression part in the axial direction is less than or equal to 1/2.

Further, a ratio of the first distance to a length of the compression portion in the axial direction is 1/4.

Further, the shell comprises an air inlet pipe, and one end of the air inlet pipe, which is far away from the motor, is used as an air inlet;

the first interface is arranged on the air inlet pipe.

Furthermore, the first interface is arranged at one end of the air inlet pipe close to the motor.

Further, a switch valve is arranged on the bypass pipeline and is configured to be switched between an opening state and a closing state;

when the switch valve is open, the fluid is configured to flow from the second port to the first port;

when the on-off valve is closed, the communication relation between the first port and the second port is cut off.

Further, the compressor also comprises a controller and a temperature sensor, wherein the temperature sensor and the switch valve are both electrically connected to the controller;

the temperature sensor is arranged in the motor cavity and used for detecting a temperature signal in the motor cavity and sending the temperature signal to the controller; the controller is used for receiving a temperature signal and sending an opening signal or a closing signal to the switch valve according to the temperature signal.

Further, the ratio of the pressure value of the second interface to the pressure value of the first interface is greater than or equal to 1.2 and less than or equal to 1.8.

According to a second aspect of the present application, there is provided a heat exchange system comprising a first heat exchanger, a second heat exchanger and the compressor described above;

the heat exchange system is configured to be switched between a cooling state and a heating state;

when the heat exchange system is in the refrigeration state, the inlet of the compressor is communicated with the outlet of the second heat exchanger, and the outlet of the compressor is communicated with the inlet of the first heat exchanger;

when the heat exchange system is in the heating state, the inlet of the compressor is communicated with the outlet of the first heat exchanger, and the outlet of the compressor is communicated with the inlet of the second heat exchanger.

The technical scheme provided by the application can comprise the following beneficial effects:

in the arrangement, the refrigerant which is positioned in the compressor and flows through the peripheral side of the motor can flow into the circulation space again through the bypass pipeline from the first interface and flow through the motor again, so that the motor is cooled for many times, the motor is prevented from being damaged due to temperature, and the compressor is protected.

It is to be understood that both the foregoing general description and the following detailed description are exemplary and explanatory only and are not restrictive of the disclosure.

Drawings

Fig. 1 is a schematic structural diagram of a heat exchange system in an embodiment of the present application.

Fig. 2 is a schematic sectional view of a compressor according to an embodiment of the present application.

Description of the reference numerals

Heat exchange system 10

Compressor 100

Casing 110

Air inlet 111

Air outlet 112

Flow-through space 113

Rotor cavity 114

Motor cavity 115

Intake pipe 116

Air outlet pipe 117

Motor 120

Stator 121

Rotor 122

First end 123

Second end 124

Screw assembly 130

Male screw 131

Drive shaft 1311

Power input unit 1312

Extrusion compression part 1313

Bearing 1314

Female screw 132

Bypass line 140

First interface 141

Second interface 142

On-off valve 143

Main flow direction X

Auxiliary flow direction Y

First heat exchanger 200

First pipe port 201

Second conduit port 202

Second heat exchanger 300

Third conduit port 301

Fourth pipe orifice 302

Fifth pipe port 303

Oil separator 400

Fluid inlet tube 420

Refrigerant outlet pipe 430

Reversing valve 500

Economizer 600

Detailed Description

Reference will now be made in detail to the exemplary embodiments, examples of which are illustrated in the accompanying drawings. When the following description refers to the accompanying drawings, like numbers in different drawings represent the same or similar elements unless otherwise indicated. The manner in which the following exemplary embodiments are described does not represent all manner of consistency with the present application. Rather, they are merely examples of apparatus consistent with certain aspects of the present application, as detailed in the appended claims.

The terminology used herein is for the purpose of describing particular embodiments only and is not intended to be limiting of the application. Unless otherwise defined, technical or scientific terms used herein shall have the ordinary meaning as understood by those of ordinary skill in the art to which this application belongs. The use of "first," "second," and similar terms in the description and in the claims does not indicate any order, quantity, or importance, but rather is used to distinguish one element from another. Similarly, the terms "a" or "an" and the like do not denote a limitation of quantity, but rather denote the presence of at least one, and if only "a" or "an" is denoted individually. "plurality" or "a number" means two or more. Unless otherwise indicated, "front", "rear", "lower" and/or "upper" and the like are for convenience of description and are not limited to one position or one spatial orientation. The word "comprising" or "comprises", and the like, means that the element or item listed as preceding "comprising" or "includes" covers the element or item listed as following "comprising" or "includes" and its equivalents, and does not exclude other elements or items. The terms "connected" or "coupled" and the like are not restricted to physical or mechanical connections, but may include electrical connections, whether direct or indirect. As used in this specification and the appended claims, the singular forms "a", "an", and "the" are intended to include the plural forms as well, unless the context clearly indicates otherwise. It should also be understood that the term "and/or" as used herein refers to and encompasses any and all possible combinations of one or more of the associated listed items.

The embodiments of the present application will be described in detail below with reference to the accompanying drawings. Features in the embodiments described below may be combined with each other without conflict.

As shown in fig. 1, the present application relates to a heat exchange system 10, the heat exchange system 10 including a compressor 100, a first heat exchanger 200, a second heat exchanger 300, and an oil separator 400. In the example of fig. 1, the heat exchange system 10 is an air-cooled heat pump chiller, although in other embodiments, the heat exchange system 10 may be a water-cooled chiller.

The heat exchange system 10 is configured to switch between a cooling state and a heating state. The heat exchange system 10 may also be provided with a reversing valve 500 and an economizer 600. The reversing valve 500 may change the communication relationship of the first heat exchanger 200, the second heat exchanger 300, and the compressor 100. The economizer 600 can achieve sub-cooling of the refrigerant. The fluid flowing out of the compressor 100 is a mixed fluid of refrigerant and oil, and the oil separator 400 may separate the fluid flowing out of the compressor 100 to supply the refrigerant to the first heat exchanger 200 or the second heat exchanger 300, so that the oil flows back to the compressor 100 through the oil supply passage 401.

When the heat exchange system 10 is in a refrigeration state, the outlet of the first heat exchanger 200 is communicated with the inlet of the second heat exchanger 300; the outlet of the second heat exchanger 300 is communicated with the inlet of the compressor 100; the outlet of the compressor 100 communicates with the fluid inlet pipe 420 of the oil separator 400 to provide the refrigerant-oil mixed fluid to the oil separator 400; the refrigerant outlet pipe 430 of the oil separator 400 communicates with the inlet of the first heat exchanger 200 to supply the refrigerant in a liquid state to the first heat exchanger 200. In other words, the outlet of the compressor 100 communicates with the inlet of the first heat exchanger 200 through the oil separator 400. At this time, the first heat exchanger 200 functions as a condenser, and the second heat exchanger 300 functions as an evaporator.

When the heat exchange system 10 is in a heating state, the outlet of the second heat exchanger 300 is communicated with the inlet of the first heat exchanger 200; the outlet of the first heat exchanger 200 is communicated with the inlet of the compressor 100; the outlet of the compressor 100 is communicated with the fluid inlet pipe 420 of the oil separator 400, and the refrigerant-oil mixed fluid is provided for the oil separator 400; the refrigerant outlet pipe 430 of the oil separator 400 communicates with the inlet of the second heat exchanger 300 to supply the gaseous refrigerant to the second heat exchanger 300. In other words, the outlet of the compressor 100 communicates with the inlet of the second heat exchanger 300 through the oil separator 400. At this time, the first heat exchanger 200 serves as an evaporator, and the second heat exchanger 300 serves as a condenser.

It should be noted that the fluid inlet pipe 420 is always connected to the outlet of the compressor 100, so that the pressure of the fluid inlet pipe 420 is always greater than that of the refrigerant outlet pipe 430. Meanwhile, in actual use, the first heat exchanger 200 includes two pipe ports, and the second heat exchanger 300 includes three pipe ports. The two pipe ports of the first heat exchanger 200 are referred to as a first pipe port 201 and a second pipe port 202. The three tube ports of the second heat exchanger 300 are referred to as a third tube port 301, a fourth tube port 302, and a fifth tube port 303. When the heat exchange system 10 is in a cooling state, the refrigerant flows into the first heat exchanger 200 from the first pipe port 201 and flows out of the first heat exchanger 200 from the second pipe port 202. The refrigerant flows into the second heat exchanger 300 from the third pipe port 301 and flows out of the second heat exchanger 300 from the fourth pipe port 302. At this time, the first pipe port 201 serves as an inlet of the first heat exchanger 200, and the second pipe port 202 serves as an outlet of the first heat exchanger 200. At this time, the third pipe port 301 serves as an inlet of the second heat exchanger 300, and the fourth pipe port 302 serves as an outlet of the second heat exchanger 300. Conversely, when the heat exchange system 10 is in the heating state, the refrigerant flows out of the first heat exchanger 200 from the first pipe port 201 and flows into the first heat exchanger 200 from the second pipe port 202. The refrigerant flows out of the second heat exchanger 300 from the fifth pipe port 303 and flows into the second heat exchanger 300 from the fourth pipe port 302. At this time, the first pipe port 201 serves as an outlet of the first heat exchanger 200, and the second pipe port 202 serves as an inlet of the first heat exchanger 200. At this time, the fifth pipe port 303 serves as an outlet of the second heat exchanger 300, and the fourth pipe port 302 serves as an inlet of the second heat exchanger 300. Of course, in other embodiments, four or other numbers of pipe ports may be provided in the first heat exchanger 200 and the second heat exchanger 300, and when the heat exchange system 10 is in different states, different pipe ports are used as the outlets or inlets of the first heat exchanger 200 and the second heat exchanger 300.

In the present embodiment, as shown in fig. 2, the compressor 100 is configured to compress fluid, and the compressor 100 includes a housing 110, a motor 120, and a screw assembly 130.

The housing 110 includes an air inlet 111 and an air outlet 112, and a flow space 113 for flowing a fluid is provided inside the housing 110. The refrigerant can enter the flow space 113 inside the casing 110 from the inlet 111 and flow out of the casing 110 from the outlet 112, with the flow direction being the main flow direction X shown in fig. 2. Accordingly, the air inlet 111 of the casing 110 is an inlet of the compressor 100, and the air outlet 112 of the casing 110 is an outlet of the compressor 100.

The housing 110 further includes a rotor chamber 114 and a motor chamber 115, the rotor chamber 114 communicates with the motor chamber 115, and the rotor chamber 114 is distant from the air inlet 111 with respect to the motor chamber 115. In other words, the refrigerant entering the compressor 100 from the inlet 111 passes through the motor chamber 115 and then passes through the rotor chamber 114. The air inlet 111, the motor chamber 115, the rotor chamber 114, and the air outlet 112 are connected and communicated to form the flow space 113.

Both the motor 120 and the screw assembly 130 are disposed inside the housing 110, and the motor 120 is configured to rotate the screw assembly 130. Specifically, the motor 120 is disposed in the motor cavity 115 and is disposed inside the housing 110 at a side close to the air inlet 111. The screw assembly 130 is disposed in the rotor chamber 114 and on a side of the interior of the housing 110 adjacent to the air outlet 112. The motor 120 includes a stator 121 and a rotor 122, the stator 121 is fixed to the housing 110, and the rotor 122 is rotatably disposed inside the stator 121 in the axial direction. The screw assembly 130 includes a male screw 131 and a female screw 132 engaged with each other, the male screw 131 includes a driving shaft 1311, and the driving shaft 1311 is fixedly connected to the rotor 122 of the motor 120, so that the motor 120 can drive the male screw 131 to rotate. The male screw 131 is engaged with the female screw 132, and the male screw 131 drives the female screw 132 to rotate, so that the volume of the inter-tooth elements changes, thereby compressing the fluid entering the inter-tooth elements in the screw assembly 130.

The compressor 100 mainly compresses a refrigerant introduced thereinto. Since the refrigerant carries a part of the oil used for the normal operation of the motor 120 during the movement, the compressor 100 may also compress the oil carried by the refrigerant.

During normal operation of the heat exchange system 10, the motor 120 in the compressor 100 rotates and drives the male screw 131 in the screw assembly 130 to rotate, thereby compressing the fluid flowing through the compressor 100. In this process, the temperature of the motor 120 increases. When the compressor 100 is operated at the minimum load, at some operating points, the temperature of the motor 120 may be too high, and the winding insulation in the motor 120 may be damaged due to the too high temperature, so that the compressor 100 may be burned out, and the service life of the compressor 100 and the stability of the heat exchange system 10 may be seriously affected.

In the present embodiment, the compressor 100 further includes a bypass conduit 140. The bypass conduit 140 includes a first port 141 and a second port 142. The first port 141 and the second port 142 are opened in the case 110 and communicate with the flow-through space 113. The bypass conduit 140 is configured to transfer fluid from the second port 142 to the first port 141. In other words, the flow direction of the refrigerant located in the bypass pipe 140 is the auxiliary flow direction Y. The motor 120 includes a first end 123 close to the air inlet 111 and a second end 124 close to the air outlet 112, the first interface 141 is located between the first end 123 of the motor and the air inlet 111 of the housing 110, and the second interface 142 is located between the second end 124 of the motor 120 and the air outlet 112 of the housing 110.

In the above arrangement, the bypass pipe 140 is provided, so that the refrigerant flowing through the circumferential side of the motor 120 in the circulation space 113 of the compressor 100 can flow into the bypass pipe 140 from the second port 142, and after passing through the bypass pipe 140, the refrigerant can flow into the circulation space 113 again from the first port 141. The main flow direction X of the refrigerant in the flow-through space 113 is opposite to the auxiliary flow direction Y of the refrigerant in the bypass pipe 140. Since the second port 142 is located at the rear end of the motor 120 and the first port 141 is located at the front end of the motor 120, the second port 142 of the bypass pipe 140 can absorb the refrigerant that has flowed through the motor 120 and supercooled the motor 120, and the refrigerant can flow into the circulation space 113 again through the first port 141 of the bypass pipe 140 and flow through the motor 120 again, so that the motor 120 can be cooled many times, the motor 120 is prevented from being damaged due to an excessively high temperature, and the compressor 100 is protected. Meanwhile, the refrigerant is repeatedly utilized for many times, so that the waste of the amount of the refrigerant can be avoided.

The direction in which the front end and the rear end correspond to each other here is a main flow direction X of the refrigerant in the flow space 113 of the casing 110.

Further, a second port 142 is located in the rotor chamber 114 and communicates with the rotor chamber 114. In the above arrangement, since the refrigerant in the rotor chamber 114 is compressed through the screw assembly 130, the pressure in the rotor chamber 114 is relatively large. The second port 142 is communicated with the rotor chamber 114, so that the refrigerant can smoothly flow from the second port 142 to the first port 141 in the auxiliary flow direction Y, and then flow through the motor 120 again, and secondarily cool the motor 120. Of course, in other embodiments, the second port 142 may be located in the motor cavity 115 and communicate with the motor cavity 115. In this case, a pressurizing pump needs to be added to the bypass line 140 so that the refrigerant flows into the second port 142 with sufficient power and flows into the first port 141 in the auxiliary flow direction Y.

Further, the screw assembly 130 includes a power input 1312 and a compression 1313. The power input portion 1312 serves to receive a driving force of the motor 120 and transmit it to the compressing and compressing portion 1313, and the compressing and compressing portion 1313 receives the driving force and rotates to compress fluid. The drive shaft 1311 of the male screw 131 serves as the power input unit 1312. The male screw 131 and the female screw 132 each include a middle portion having teeth on the circumferential surface thereof, and a bottom portion fixed to the bearing 1314. The male screw 131 and the female screw 132 are engaged at their middle portions to form the above-mentioned compression part 1313. The projection of the second interface 142 on the screw assembly 130 is located on the extrusion compression part 1313, the projection is located at a first distance d1 from one end of the extrusion compression part 1313 close to the power input part 1312, and the ratio of the first distance to the length d2 of the extrusion compression part 1313 in the axial direction is smaller than or equal to 1/2. The compression compressing part 1313 may compress the refrigerant therein, and the refrigerant may increase in pressure during the compression, thereby facilitating the flow of the refrigerant from the second port 142 to the first port 141. However, the closer to the side of the compression compressing portion 1313 away from the power input portion 1312, the more the refrigerant is compressed, so that the temperature of the refrigerant may also be raised. If the refrigerant having an excessively high temperature flows back to the flow space 113 through the bypass pipe 140 and secondarily cools the motor 120, the cooling efficiency of the refrigerant to the motor may be reduced. By controlling the position of the second interface 142, the backflow of the refrigerant with an excessively high temperature can be avoided, thereby improving the cooling effect, further ensuring the service life of the motor 120 and the compressor 100, and improving the stability and reliability of the heat exchange system 10.

The distance projected to the end of the squeeze compressor 1313 close to the power input unit 1312 described here is the distance from the center of the projection to the end of the squeeze compressor 1313 close to the power input unit 1312.

It has been proved through a lot of experiments that when the ratio of the first distance d1 to the length d2 of the pressing and compressing part 1313 in the axial direction is 1/4, the refrigerant entering the bypass pipe 140 through the second port 142 has enough power to overcome the pressure on the first port 141 and the second port 142 and the resistance in the bypass pipe 140, to realize the flow from the second port 142 to the first port 141 and enter the motor cavity 115 in the flow-through space 113 to cool the motor 120. Meanwhile, the part of the refrigerant is compressed by the compression part 1313 of the screw assembly 130 to a relatively low degree, and the temperature is still in a relatively low range, so that the refrigerant can effectively cool the motor 120 after flowing back through the bypass pipe 140.

Further, the ratio of the pressure value of the second port 142 to the pressure value of the first port 141 is greater than or equal to 1.2, and is less than or equal to 1.8. It is proved through a lot of experiments that when the ratio of the pressure value of the second port 142 to the pressure value of the first port 141 is within the above range, it can be ensured that the refrigerant can overcome the resistance in the bypass pipe 140, flow from the second port 142 to the first port 141, and finally flow into the circulation space 113. The ratio of the pressure value of the second port 142 to the pressure value of the first port 141 is within the above range by controlling the positions of the second port 142 and the first port 141, and the ratio of the pressure value of the second port 142 to the pressure value of the first port 141 is within the above range by arranging a pressure pump on the bypass pipe 140. In the present embodiment, the ratio of the pressure value of the second port 142 to the first port 141 is 1.5, so as to ensure that the refrigerant can flow from the second port 142 to the first port 141 against the resistance. Meanwhile, energy waste is avoided.

Further, the housing 110 further includes an inlet pipe 116 and an outlet pipe 117. One end of the air inlet pipe 116 away from the motor 120 serves as an air inlet 111, and one end of the air outlet pipe 117 away from the motor 120 serves as an air outlet 112. The first port 141 opens to the intake pipe 116. In the above arrangement, the intake pipe 116 is simple in structure, and has no other parts therein. The process of opening the first port 141 in the intake pipe 116 is simple.

Specifically, the first port 141 is opened at an end of the intake pipe 116 close to the motor 120. Through the above arrangement, the length of the bypass pipe 140 can be shortened, so that the resistance to be overcome when the refrigerant flows through the bypass pipe 140 is reduced, and the refrigerant can be secondarily cooled through the bypass pipe 140 with less energy, which means that the degree of compression of the refrigerant by the screw assembly 130 can be properly reduced, the temperature thereof can be relatively low, and the cooling efficiency of the motor 120 can be improved. In other words, the projection of the second interface 142 on the extrusion compression part 1313 may be located on a side of the extrusion compression part 1313 close to the motor 120.

Further, the bypass pipe 140 is provided with an on-off valve 143, and the on-off valve 143 is configured to be switched between an open state and a closed state. When the on-off valve 143 is opened, fluid is configured to flow from the second port 142 to the first port 141. When the on-off valve 143 is closed, the communication relationship between the first port 141 and the second port 142 is cut off. By controlling the opening and closing of the switching valve 143, the flow of the refrigerant in the bypass pipe 140 can be controlled. When the temperature of the motor 120 is too high, the switch valve 143 is switched to an open state, and a part of the refrigerant flows back and cools the motor 120. When the temperature of the motor 120 is within a reasonable range, the switching valve 143 is switched to the closed state, and the refrigerant flows only in the circulation space 113 and is supplemented to the first heat exchanger 200 or the second heat exchanger 300. Through the arrangement, when the temperature of the motor 120 is within a reasonable range, the circulation of the refrigerant in the bypass pipeline 140 can be avoided, so that the waste of energy is avoided, and the operation efficiency of the heat exchange system 10 is improved.

The compressor 100 also includes a controller (not shown) and a temperature sensor (not shown). The temperature sensor and the switch valve 143 are electrically connected to the controller. The temperature sensor is disposed in the motor cavity 115 and configured to detect a temperature signal in the motor cavity 115 and send the temperature signal to the controller. The controller is used for receiving the temperature signal sent by the temperature sensor and sending an opening signal or a closing signal to the switch valve 143 according to the temperature signal. When the on-off valve 143 receives the on signal, the on-off valve 143 is switched to the on state; when the on-off valve 143 receives the off signal, the on-off valve 143 is switched to the off state. Through the arrangement, the temperature of the motor 120 can be intelligently controlled, so that the service lives of the motor 120 and the compressor 100 are ensured, and the reliability of the heat exchange system 10 is improved.

Although the present application has been described with reference to a preferred embodiment, it should be understood that various changes, substitutions and alterations can be made herein without departing from the spirit and scope of the application, and all changes, substitutions and alterations that fall within the spirit and scope of the application are to be understood as being covered by the following claims.

Claims (10)

1. A compressor configured to compress a fluid, the compressor comprising:

a motor;

the motor is arranged in the shell, the shell comprises an air inlet and an air outlet, and a circulation space for fluid to flow is arranged in the shell;

the bypass pipeline comprises a first interface and a second interface, and the first interface and the second interface are arranged on the shell and communicated with the circulation space; the bypass conduit is configured to transfer fluid from the second port to the first port;

the motor comprises a first end close to the air inlet and a second end close to the air outlet, the first interface is located between the first end of the motor and the air inlet of the shell, and the second interface is located between the second end of the motor and the air outlet of the shell.

2. The compressor of claim 1, wherein the housing further includes a rotor cavity and a motor cavity, the motor being disposed in the motor cavity, the rotor cavity communicating with the motor cavity and being distal from the inlet port relative to the motor cavity;

the second port is located in the rotor cavity.

3. The compressor of claim 2, further comprising a screw assembly disposed in the rotor cavity; the screw assembly comprises a power input part and an extrusion compression part;

the projection of the second interface on the screw assembly is located an extrusion compression part, the distance from the projection to one end of the extrusion compression part close to the power input part is a first distance, and the ratio of the first distance to the length of the extrusion compression part in the axial direction is less than or equal to 1/2.

4. The compressor of claim 3, wherein a ratio of the first distance to a length of the compression portion in the axial direction is 1/4.

5. The compressor of claim 1, wherein the housing includes an intake duct, an end of the intake duct remote from the motor serving as an intake port;

the first interface is arranged on the air inlet pipe.

6. The compressor of claim 5, wherein the first port opens at an end of the intake tube proximate the motor.

7. The compressor of claim 1, wherein the bypass conduit is provided with an on-off valve configured to switch between an open state and a closed state;

when the switch valve is open, the fluid is configured to flow from the second port to the first port;

when the on-off valve is closed, the communication relation between the first port and the second port is cut off.

8. The compressor of claim 7, further comprising a controller and a temperature sensor, wherein the temperature sensor and the on-off valve are both electrically connected to the controller;

the shell further comprises a rotor cavity and a motor cavity, the motor is arranged in the motor cavity, the temperature sensor is arranged in the motor cavity, and the temperature sensor is used for detecting a temperature signal in the motor cavity and sending the temperature signal to the controller; the controller is used for receiving a temperature signal and sending an opening signal or a closing signal to the switch valve according to the temperature signal.

9. The compressor of claim 1, wherein a ratio of the pressure value of the second port to the pressure value of the first port is equal to or greater than 1.2 and equal to or less than 1.8.

10. A heat exchange system comprising a first heat exchanger, a second heat exchanger and a compressor according to any one of claims 1 to 9;

the heat exchange system is configured to be switched between a cooling state and a heating state;

when the heat exchange system is in the refrigeration state, the inlet of the compressor is communicated with the outlet of the second heat exchanger, and the outlet of the compressor is communicated with the inlet of the first heat exchanger;

when the heat exchange system is in the heating state, the inlet of the compressor is communicated with the outlet of the first heat exchanger, and the outlet of the compressor is communicated with the inlet of the second heat exchanger.

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